Orificed check valve in wing circuit

ABSTRACT

A wing locking system for a harvesting header is provided. The wing locking system includes an accumulator, a fluid cylinder operably attached to a wing of the harvesting header, a hose fluidly connecting the accumulator and the fluid cylinder, and a valve operably disposed between the accumulator and the fluid cylinder. The valve includes a first selectable position configured to permit a first fluid flow rate between the accumulator and the fluid cylinder and a second selectable position configured to permit a second fluid flow rate from the accumulator to the fluid cylinder. The first fluid flow rate is greater than the second fluid flow rate.

FIELD OF THE DISCLOSURE

The present disclosure relates to agricultural harvesters, and, moreparticularly, to a system configured to facilitate hydraulic locking ofa harvester header having pivoting wings using a blocker valve with anopen free flow state and an orificed check valve state.

BACKGROUND

Crop harvesting is commonly performed by a harvesting system comprisinga combine harvester (“combine”) equipped with a removable headerdesigned for harvesting crops. In an attempt to increase the throughputof such harvesting systems, combines are being paired with increasinglywider headers. However, although the increased span of such widerheaders may improve throughput by increasing the rate at which groundcan covered by the harvesting system, the increased width of the headermay result in a decrease in crop yield efficiency. In particular, giventhe rigid, flat configuration of headers typically used in suchharvesting systems, the increased inability of wider, rigid frame headerto conform to variations in terrain often results in a decrease in theamount of crop that is harvested as the harvesting system travels overuneven terrain.

Additionally, increasing the width of the header of a harvesting systemoften increases the structural loads imparted by the heavier, widerheader onto the combine. As a result, many combines that are used insuch wider header harvesting systems incorporate reinforced combinestructures configured to support the added weight of a wider header andto withstand and resist the increased dynamic loads that such widerheaders impart. In addition to increasing the material costs required tomanufacture such reinforced combines, the added mass of such reinforcedcombines also typically increases the costs of operating the harvestingsystem.

SUMMARY

One implementation of the present disclosure is a wing locking systemfor a harvesting header. The wing locking system includes anaccumulator, a fluid cylinder operably attached to a wing of theharvesting header, a hose fluidly connecting the accumulator and thefluid cylinder, and a valve operably disposed between the accumulatorand the fluid cylinder. The valve includes a first selectable positionconfigured to permit a first fluid flow rate between the accumulator andthe fluid cylinder and a second selectable position configured to permita second fluid flow rate from the accumulator to the fluid cylinder. Thefirst fluid flow rate is greater than the second fluid flow rate.

The second selectable position of the valve may permit fluid flow fromthe accumulator to the fluid cylinder through an orificed check valveand may prevent fluid flow from the fluid cylinder to the accumulator.When the valve is in the second selectable position, the flow of fluidinto the fluid cylinder may be configured to constrain an upward pivotangle of the wing. In some embodiments, the valve may be in the secondselectable position when the harvesting header encounters a negativeloading condition. The upward pivot angle of the wing may range from0.05° to 1.0°. In other embodiments, the valve may be in the secondselectable position when the harvesting header is in an integratedtransport configuration. The upward pivot angle of the wing may rangefrom 1.0° to 10.0° and may be constrained by a limitation of the fluidcylinder.

Another implementation of the present disclosure is method of operatinga harvesting header. The harvesting header includes a center section, aleft wing hingedly attached to the center section, a right wing hingedlyattached to the center section, and a wing locking system. The winglocking system includes an accumulator, a fluid cylinder operablyattached to at least one of the left wing and the right wing, a hosefluidly connecting the accumulator and the fluid cylinder, and a valveoperably disposed between the accumulator and the fluid cylinder. Thevalve includes a first selectable position configured to permit a firstfluid flow rate between the accumulator and the fluid cylinder and asecond selectable position configured to permit a second fluid flow ratefrom the accumulator to the fluid cylinder. The first fluid flow rate isgreater than the second fluid flow rate. The method further includesoperating the valve in the second selectable position during at leastone of a transient negative loading condition and a sustained negativeloading condition caused by an integrated transport configuration of theharvesting header.

The second selectable position may permit fluid flow from theaccumulator to the fluid cylinder through an orificed check valve andmay prevent fluid flow from the fluid cylinder to the accumulator. Insome embodiments, the flow of fluid from the hose into the fluidcylinder may cause at least one of the left wing and the right wing topivot upwards relative to the center section by between approximately0.05° and approximately 1.0° during the transient negative loadingcondition of the harvesting header. In other embodiments, the flow offluid from the hose into the fluid cylinder may cause at least one ofthe left wing and the right wing to pivot upwards relative to the centersection by between approximately 1.0° and approximately 10.0° during thesustained negative loading condition caused by the integrated transportconfiguration of the harvesting header.

In some embodiments, when the valve is in the first selectable position,the flow of fluid into the fluid cylinder and out of the fluidaccumulator and out from the fluid cylinder and into the fluidaccumulator may be configured to allow the fluid cylinder to move the atleast one wing within a first range along a wing trajectory. When thevalve is in the second selectable position, the flow of fluid out fromthe fluid accumulator into the fluid cylinder may be configured to allowthe fluid cylinder to move the at least one wing within a second rangealong the wing trajectory. The second range may be smaller than thefirst range.

In some embodiments, the transient negative loading condition may becaused by uneven terrain. In other embodiments, the transient negativeloading condition may be caused by flexure of a trailer transporting theharvesting head. In further embodiments, when the harvesting head is inthe integrated transport configuration, the harvesting head may besupported by structural members and ground engaging wheels.

Yet another implementation of the present disclosure is a harvestersystem. The harvester system includes a center section, a left winghingedly attached to the center section, a right wing hingedly attachedto the center section, and a wing locking system. The wing lockingsystem includes an accumulator, a fluid cylinder operably attached to atleast one of the left wing and the right wing, a hose fluidly connectingthe accumulator and the fluid cylinder, and a valve operably disposedbetween the accumulator and the fluid cylinder. The valve includes afirst selectable position configured to permit a first fluid flow ratebetween the accumulator and the fluid cylinder and a second selectableposition configured to permit a second fluid flow rate from theaccumulator to the fluid cylinder. The first fluid flow rate is greaterthan the second fluid flow rate.

The second selectable position of the valve may permit fluid flow fromthe accumulator to the fluid cylinder through an orificed check valveand may prevent fluid flow from the fluid cylinder to the accumulator.In some embodiments, the flow of fluid from the hose into the fluidcylinder may cause at least one of the left wing and the right wing topivot upwards relative to the center section by between approximately0.05° and approximately 1.0° during a transient negative loadingcondition. In other embodiments, the flow of fluid from the hose intothe fluid cylinder may cause at least one of the left wing and the rightwing to pivot upwards relative to the center section by betweenapproximately 1.0° and approximately 10.0° during a sustained negativeloading condition caused by an integrated transport configuration of theharvesting header. In further embodiments, the harvester system mayinclude structural members and ground engaging wheels.

Those skilled in the art will appreciate that the summary isillustrative only and is not intended to be in any way limiting. Otheraspects, inventive features, and advantages of the devices and/orprocesses described herein, as defined solely by the claims, will becomeapparent in the detailed description set forth herein and taken inconjunction with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIGS. 1A-1C illustrate a harvester in a harvesting configurationtravelling over different types of terrain, according to someembodiments.

FIG. 2 is a simplified block diagram illustrating a top view of aheader, according to some embodiments.

FIG. 3 illustrates a harvester in a non-harvesting transportconfiguration, according to some embodiments.

FIG. 4 is a simplified general block diagram illustrating a suspensionsystem, according to some embodiments.

FIGS. 5A-5C are simplified general block diagrams illustrating a blockervalve, according to some embodiments.

FIG. 6A is a simplified general block diagram illustrating a suspensionsystem during a harvesting configuration of a harvester, according tosome embodiments.

FIG. 6B is a simplified general block diagram illustrating a front viewof a header during the harvesting configuration of the harvester shownin FIG. 6A, according to some embodiments.

FIG. 7A is a simplified general block diagram illustrating a suspensionsystem during a transition configuration of a harvester, according tosome embodiments.

FIG. 7B is a simplified general block diagram illustrating a front viewof a header during the transition configuration of the harvester shownin FIG. 7A, according to some embodiments.

FIG. 8A is a simplified general block diagram illustrating a suspensionsystem during a non-harvesting transport configuration of a harvester,according to some embodiments.

FIG. 8B is a simplified general block diagram illustrating a front viewof a header during the non-harvesting transport configuration of theharvester shown in FIG. 8A, according to some embodiments.

FIG. 9A is a simplified general block diagram illustrating a suspensionsystem during a downward flex configuration of a harvester, according tosome embodiments.

FIG. 9B is a simplified general block diagram illustrating a front viewof a header during the downward flex configuration of the harvestershown in FIG. 9A, according to some embodiments.

FIG. 10A is a simplified general block diagram illustrating a suspensionsystem during an upward flex configuration of a harvester, according tosome embodiments.

FIG. 10B is a simplified general block diagram illustrating a front viewof a header during the upward flex configuration of the harvester shownin FIG. 10A, according to some embodiments.

FIG. 11 illustrates a harvester in an integrated transport harvestingconfiguration, according to some embodiments.

FIG. 12A is a simplified general block diagram illustrating a suspensionsystem during an integrated transport harvesting configuration,according to some embodiments.

FIG. 12B is a simplified general block diagram illustrating a front viewof a header during the integrated transport harvesting configurationshown in FIG. 12A, according to some embodiments.

DETAILED DESCRIPTION

Referring generally to the FIGURES, a suspension system 200 for aharvester 100 configured to reduce structural loads is shown. As will bedescribed in more detail below, suspension system 200 is configured as avariable spring rate suspension system, which allows the header 104 tomore closely and easily follow terrain while the harvester 100 is in aharvesting mode, while also providing the header 104 with the ability toflex during an elevated, non-harvesting transport configuration of theheader 104. In doing so, the suspension system 200 reduces thestructural loads that the combine 102 supporting the header 104 issubject to during operation of the harvester 100. As such, thesuspension system 200 allows the width of the header 104 to be increased(so as to, e.g., increase harvesting throughput) without requiringreinforcement of the structure of the combine 102 to support theincreased mass of the wider header 104.

Referring to FIGS. 1A-1C, an agricultural harvester 100 according to oneembodiment is shown in various harvesting configurations as theharvester 100 travels over terrain having varying contours. Asillustrated in FIGS. 1A-1C, according to various embodiments, theharvester 100 includes a combine 102 and an agricultural harvestingheader 104 supported on the front of the combine 102.

As illustrated by the simplified block diagram of FIG. 2, according tovarious embodiments, the header 104 defines an articulated structurecomprising a center section 142 to which a left wing 144 a is hingedlyconnected by a left hinge joint 146 a and to which a right wing 144 b ishingedly connected by a right hinge joint 146 b. The connection of theleft wing 144 a to the center section 142 via left hinge joint 146 aallows the left wing 144 a to pivot upwards or downwards relative to thecenter section 142 about a generally horizontal axis along which theleft hinge joint 146 a extends. Similarly, the connection of the rightwing 144 b to the center section 142 via right hinge joint 146 b allowsthe right wing 144 b to pivot upwards or downwards relative to thecenter section 142 about a generally horizontal axis along which theright hinge joint 146 b extends. As will be understood, given theindependent hinged attachment of each of the left wing 144 a and theright wing 144 b to the center section 142, the left wing 144 a maypivot in any direction (i.e. upwardly or downwardly) and to any degree,irrespective of any pivoting of the right wing 144 b about the centersection 142, and vice versa.

Although, as described below, the harvester 100 comprises a suspensionsystem 200 configured to maintain the header 104 in a generally flatconfiguration, according to some embodiments, such as, e.g., illustratedin FIG. 2, a manually or automatically actuated lock 148 may be providedbetween left wing 144 a and center section 142 and/or between right wing144 b and center section 142 which may optionally be used in situationsin which a user may desire to fixedly and rigidly restrain the pivotingmovement of left wing 144 a and/or right wing 144 b relative to thecenter section 142.

As the harvester 100 transitions from travelling along generally flatterrain (during which the center section 142, left wing 144 a and rightwing 144 b each extend along a generally horizontal plane, such as,e.g., illustrated in FIG. 1A, that is substantially parallel to theterrain on which the header 104 is supported) to uneven terrain, thehinged connections of the left wing 144 a and right wing 144 b to thecenter section 142 allow the header 104 to more closely adapt to andconform to the contours of the variable terrain (such as, e.g.,illustrated in FIGS. 1B and 1C).

In addition to increasing crop yield, by allowing the left wing 144 aand right wing 144 b to independently flex and adapt to changingterrain, the mass of the header 104 that is accelerated as the header104 travels over uneven terrain is decreased, thereby minimizing thestructural loads on the combine 102. Thus, the articulated configurationof the header 104 allows the width of the header 104 to be increased (ascompared to a rigid, non-articulated header) without necessarilyresulting in increased stress on the combine 102, thereby obviating theneed to reinforce the combine 102 to support the wider width header 104.

The combine 102 generally includes a combine harvester vehicle 106 andfeederhouse 108 pivotally attached about a rear end to a lower portionof the combine harvester vehicle 106 (such as, e.g., to a chassis of theharvester vehicle 106). A forward end of the feederhouse 108 isconfigured to support the header 104. According to various embodiments,one or more feederhouse actuators (not shown) are operably coupledbetween the rear end of the feederhouse 108 and the combine harvestervehicle 106. The feederhouse actuators may comprise any number of knownactuator arrangements, with selective manual and/or automatic activationof the feederhouse actuator(s) being configured to cause the rear end ofthe feederhouse 108 to pivot relative to the combine harvester vehicle106, thereby resulting in a vertical movement of the forward end of thefeederhouse 108, as well as the resultant vertical movement of theattached header 104, in an upwards or downwards direction, such asillustrated, e.g., in FIG. 3.

As will be understood, the activation of these feederhouse actuators mayallow the harvester 100 to transition between a harvesting configurationin which the weight of the header 104 is at least partially supported bythe ground, to a non-harvesting transport configuration in which theheader 104 is elevated with reference to the ground (and in whichconfiguration the weight of the header 104 is supported entirely by thecombine 102), such as, e.g., illustrated in FIG. 3.

In light of the articulated configuration of the header 104, whenfeederhouse actuator(s) are activated to raise the header 104 to anelevated, non-harvesting transport configuration such as shown in FIG.3, the hinged attachment of left wing 144 a and right wing 144 b(“together, wings 144”) to center section 142 via left hinge joint 146 aand right hinge joint 146 b, respectively, may cause the outermost endsof wings 144 to sag relative to the height of center section 142. Aswill be understood, the amount of downward displacement or sag of theoutermost ends of the wings 144 as measured relative to the centersection 142 increases as the width of the wings 144 is increased.

As described above, the ability of wings 144 to pivot substantiallyrelative to center section 142 may advantageously allow the header 104to conform to the terrain during harvesting. However, such substantialpivoting movement of the wings 144 relative to the center section 142may be undesirable when the header 104 is in an elevated position (e.g.,when the harvester 100 is being turned around on end rows or duringnon-harvesting transport of the harvester 100). In particular, leavingthe wings 144 unsupported and free to pivot relative to center section142 while the header 104 is elevated may cause the outermost ends ofwings 144 to fully lower, thereby decreasing clearance to the groundeven when the header 104 is in a fully raised configuration, which mayallow inadvertent contact between the ground and header 104 that coulddamage the header 104.

Although preventing sagging of the outermost ends of the wings 144 inorder to maintain a substantially flat profile of the header 104 may bedesirable when the header 104 is in an elevated configuration such as,e.g., illustrated in FIG. 3—for reasons as described with reference torigid frame, non-articulated headers above—it may be undesirable to lockor otherwise fix the wings 144 into a substantially rigid configurationin an attempt to prevent the outermost ends of wings 144 from doing so.In particular, locking or otherwise restricting movement of the wings144 relative to the center section 142 during an elevated configurationof the header 104 (such as, e.g., during non-harvesting transport of theharvester 100) may undesirably increase the dynamic loads that areimparted by the header 104 onto the combine 102.

Instead, as will be described in more detail below, the harvester 100 isadvantageously provided with a suspension system 200 that allows forsome degree of pivoting movement of the wings 144 of the header 104relative to the center section 142 while also supporting the header 104in a substantially flat profile during field transport of the harvester100 (i.e. when the header 104 is lifted entirely off of the ground). Indoing so, the suspension system 200 minimizes the amount of header 104inertia that must be accelerated when encountering bumps in terrain,thereby reducing the forces imparted on the combine 102 during travel ofthe harvester 100 with the header 104 in an elevated configuration.

Accordingly, in various embodiments, the harvester 100 is provided witha variable spring rate suspension system 200 configured to prevent theamount of downward displacement of the outermost ends of the wings 144relative to the center section 142 when the header 104 is in an elevatedconfiguration and to allow the hingedly attached wings 144 to pivot asneeded relative to the center section 142 while the harvester 100 is ina harvesting configuration (i.e. when the header 104 is at leastpartially supported along the ground), thus minimizing the structuralloading of the combine 102 by the header 104. As such, the suspensionsystem 200 may allow the harvester 100 to incorporate a wider header 104for more efficient harvesting throughput without requiring a reinforcedcombine 102 structure to support the wider width header 104.

More specifically, according to various embodiments, when the harvester100 is in a harvesting configuration (i.e. when the header 104 is atleast partially supported by the ground, such as, e.g., illustrated inFIGS. 1A-1C) the suspension system 200 of the harvester 100 isconfigured to allow for upward and downward pivoting of the wings 144 byapproximately no more than ±15.0°, more specifically by approximately nomore than ±10.0°, and more specifically by approximately no more than±5.0° as measured relative to the lateral axis along which the centersection 142 extends. When the harvester 100 is an elevated,non-harvesting transport position (i.e. when the header 104 is elevatedsuch that the mass of the header 104 is not supported by the ground),the suspension system 200 is configured such that the upwards ordownwards pivoting of the wings 144 is constrained to betweenapproximately 10% and 30%, more specifically between approximately 15%and 25%, and even more specifically between approximately 20% of therange through which the wings 144 are allowed to pivot when theharvester 100 is in the harvesting configuration, such that the upwardand downward pivoting of the wings 144 as measured relative to thelateral axis along which the center section 142 extends is approximatelyno more than ±4.5°, more specifically is no more than approximately±2.5°, and even more specifically no more than approximately ±1.0° whenthe harvester 100 is in a non-harvesting transport position (such as,e.g., illustrated in FIG. 3). By constraining the upward or downwardpivoting of the wings 144 during harvesting and non-harvesting transportconfigurations in such a manner, the suspension system 200 is configuredto allow for between an approximately 10% to approximately 20% reductionin the stress imparted onto the combine 102 by the articulated header104, as compared to the structural load that would be imparted by arigid, non-articulated header 104 having a similar width and mass.

As will be understood, the suspension system 200 may be defined by anynumber of and combination of different components that are arranged in amanner to allow for the selective constraint of the movement of thewings 144 relative to the center section 142 according to first andsecond variable states. In particular, in the first variable state, thesuspension system 200 is configured such that movement of the wings 144is constrained to a first range (such as, e.g., described with referenceto the harvesting configuration above). Meanwhile, in the secondvariable state, the suspension system 200 is configured such thatmovement of the wings 144 is constrained to a second range that is lessthan the first range (such as, e.g., described with reference to thenon-harvesting transport configuration above).

For example, according to some embodiments (not shown), suspensionsystem 200 may comprise a first set of coiled springs positioned aboutthe left wing 144 a and a second set of coils positioned about rightwing 144 b. Each of the first set and second set of coils comprise afirst spring and a second spring. One or both of the length of the firstspring and/or spring constant of the first spring differs from thesecond spring, such that the spring force of the first spring is greaterthan the spring force of the second spring. The first and second springsare configured to be independently engageable, such that, when the firstspring is engaged, the pivoting movement of the wings 144 about centersection 142 of the header 104 is constrained to a smaller range ofmotion than when the first spring is disengaged, and the second springis engaged.

Accordingly, in such embodiments, by selectively engaging the secondsprings, the suspension system 200 may provide the wings 144 withsufficient ability to pivot about center section 142 so as to allow thewings 144 to adapt to the contours of changing terrain when theharvester 100 is in harvesting position. Meanwhile, by selectivelyengaging the first springs, the suspension system 200 may be configuredto allow for more constrained movement of the wings 144 relative to thecenter section 142, thereby minimizing the degree of displacement of theoutermost ends of the wings 144 relative to the center section 142 (andthereby minimizing the risk of the outermost ends inadvertentlycontacting the ground when the header 104 is in an elevated, transportposition) while also providing the wings 144 with sufficient flexibilityto pivot so as to minimize the dynamic loads on the combine 102 duringnon-harvesting transport of the harvester 100 (such as, e.g.,illustrated in FIG. 3).

Alternatively, in other coiled spring embodiments of suspension system200, a single coiled spring may be positioned about each of the leftwing 144 a and the right wing 144 b. The suspension system 200 mayfurther comprise a length adjusting mechanism associated with each ofthe left wing 144 a and right wing 144 b, which is selectivelyactuatable to increase or decrease the effective length of the coiledspring. During non-harvesting transport with the header 104 in anelevated transport position, the length adjusting mechanisms may beactuated to effectively shorten the lengths of the springs, therebyincreasing the spring force of the springs and minimizing the freedom ofthe wings 144 to pivot relative to center section 142. Meanwhile, whenin the harvesting position, the length adjusting mechanisms may beactuated to effectively lengthen the springs, thereby decreasing thespring forces of the springs and increasing the degree to which thewings 144 may pivot. As will be understood, according to variousembodiments, the length adjusting mechanisms may be configured to allowthe effective lengths of the springs to vary between first and secondfixed lengths, while in other embodiments, the length adjustingmechanisms may be configured to allow the effective lengths of thesprings to be varied as desired, thus allowing for greater or lesserdegrees of constraint of the movement of the wings 144 relative to thecenter section 142 of the header 104 during different non-harvestingtransport and/or harvesting uses of the harvester 100. Additionally,while in some such embodiments the length adjusting mechanisms of thewings 144 may be actuated by the suspension system 200 in tandem withone another, in other embodiments, the length adjusting mechanisms maybe actuated independent of one another, such that the degree to whichmovement of the left wing 144 a is constrained may vary from the degreeto which movement of the right wing 144 b is constrained, and viceversa.

In yet other embodiments, the suspension system 200 may comprise ahydraulic system configured to provide for first and second variablestates which selectively allow for differing degrees of pivoting of thewings 144 relative to the center section 142. For example, in someembodiments (not shown), the suspension system 200 may comprise a pair ahydraulic circuits that are operably provided for each of the left wing144 a and right wing 144 b, with a first circuit having a differentvolume and/or pressure of fluid than a second, distinct circuit definingthe pair of hydraulic circuits.

Referring to FIG. 4, a simplified schematic of a hydraulic based springsuspension system 200 comprising a blocker valve 300 which is configuredto provide for first and second variable states according to oneembodiment is illustrated. The suspension system 200 illustrated in FIG.4 corresponds to one of the left wing 144 a or right wing 144 b of theheader 104, with the other of the left wing 144 a or right wing 144 bbeing provided with a substantially similar, albeit mirrored, suspensionsystem 200 as shown in and described with reference to FIG. 4.

Suspension system 200 generally comprises a fluid cylinder 202 that isfluidly connected to one or more accumulators 206 via an attenuationhose 208. The accumulators 206 are configured to store a volume ofpressurized fluid (such as, e.g., incompressible hydraulic fluid) thatis supplied to the fluid cylinder 202 via the attenuation hose 208. Asfluid flows into or out from the fluid cylinder 202, the fluid cylinder202 is configured to extend or retract. As the fluid cylinder 202 isconfigured to suspend the wing 144 (i.e., one of left wing 144 a and/orright wing 144 b), the retraction and extension of the fluid cylinder202 in response to changes in the amount of fluid within fluid cylinder202 causes the wing 144 to move pivotably about the center section 142,resulting in the upward or downward movement of the wing 144 relative tothe center section 142.

A blocker valve 300 is fluidly disposed between the fluid cylinder 202and the accumulators 206. As will be described with more detail withreference to FIGS. 6A-9B below, the blocker valve 300 is configured toallow for selective flow of fluid between the fluid cylinder 202 and theaccumulators 206, allowing the fluid cylinder 202 to provide varyingdegrees of suspension of the wing 144, which in turn allows thesuspension system 200 to provide for first and second variable statesthat selectively allow for differing degrees of pivoting of the wings144 relative to the center section 142.

As shown in FIG. 4, the accumulators 206 are additionally fluidlyconnected to a hydraulic block 210, which serves as a source of fluidfor the accumulators 206. Fluid from the hydraulic block 210 is suppliedto the accumulators 206 in response to the selective activation of avalve 212 to permit flow between the hydraulic block 210 andaccumulators 206. Once sufficient fluid has been allowed to fill theaccumulators 206 to a desired pressure, the valve 212 may be activatedto a closed configuration. As will be understood, according to someembodiments, a single hydraulic block 210 may be common to thesuspension systems 200 of both the left wing 144 a and the right wing144 b, while in other embodiments, the suspension systems 200 of each ofthe left wing 144 a and the right wing 144 b may comprise distinct,individual hydraulic blocks 210.

Referring to FIGS. 5A-5C, a blocker valve 300 according to variousembodiments is illustrated. In general, the blocker valve 300 isselectively activatable between a flow position, defined by a flowstructure 302 and a restricted flow position defined by aflow-restriction structure 304. As will be understood, blocker valve 300may be biased to either the flow position or restricted-flow position,and may be selectively energized or otherwise activated between the flowand restricted flow positions according to any number of differentarrangements, including mechanical and/or electromechanicalarrangements.

Additionally, while in some embodiments the activation of the blockervalve 300 between the flow position and the restricted-flow position maybe controlled directly by the operator as desired, according to otherembodiments, the activation of the blocker valve 300 may be controlledby a control system of the harvester 100. For example, according to someembodiments, the harvester 100 may comprise a control system, which, inaddition to controlling other aspects of the operation of the harvester100, may additionally be configured to control the activation of theblocker valve 300. According to some such embodiments, the controlsystem may be configured to automatically activate the blocker valve 300to the restricted-flow position upon the control system exiting out ofan auto-header height mode of the control system and/or in response tothe feederhouse 108 (and attached header 104) being lifted up andelevated with respect to the ground. In yet other embodiments, thecontrol system may be configured such that, when the harvester 100 isoperated in a manual mode, the blocker valve 300 is automaticallyactivated to a restricted-flow position upon the control systemreceiving a signal from ground detection sensors that the header 104 hasbeen elevated off of the ground.

When the blocker valve 300 is in the restricted-flow position, fluidpresent within the fluid cylinder 202 and attenuation hose 208 isprevented from flowing into the accumulators 206. However, as will bedescribed in more detail below with reference to FIGS. 10A-12B,according to some embodiments, it may be advantageous to allow for alimited degree of fluid flow from the accumulators 206 into theattenuation hose 208 and fluid cylinder 202. Accordingly, as shown inFIG. 5A, according to some embodiments, the flow-restriction structure304 of blocker valve 300 may comprise an orificed check valve structure400, which is configured to restrict flow from the attenuation hose 208and fluid cylinder 202 into the accumulators 206, but which allows forflow from the accumulators 206 into the attenuation hose 208, even whenthe blocker valve 300 is in the restricted flow position.

In other embodiments, it may be desired that there be no flow in eitherdirection (i.e. no flow of fluid into or out of the accumulators 206)when the blocker valve 300 is in the restricted flow position. Accordingto some such embodiments, the flow-restriction structure 304 of blockervalve 300 may comprise a double-checked valve structure (such as, e.g.,illustrated in FIG. 5B) or other structure configured to prevent flow ineither direction through the blocker valve 300.

As shown in FIG. 5C, in some embodiments in which the blocker valve 300comprises a flow-restriction structure 304 configured to prevent flow ineither direction through the blocker valve 300 (such as, e.g., adouble-checked valve flow-restriction structure 304), the suspensionsystem 200 may include an orificed check valve structure 400 arrangedfluidly in parallel with the blocker valve 300. By providing analternate fluid path through which fluid from the accumulators 206 mayflow into the attenuation hose 208, the orificed check valve structure400 may allow for restricted flow of fluid from the accumulators 206into the attenuation hose 208 even when the blocker valve 300 is in therestricted-flow position.

The ability of the suspension system 200 to provide for first and secondvariable states which selectively allow for differing degrees ofpivoting of the wings 144 relative to the center section 142 will now bedescribed with reference to FIGS. 6A-9B.

Referring to FIGS. 6A and 6B, a simplified block diagram of thesuspension system 200 and the header 104 configuration is shown duringharvesting operation of the harvester 100 according to some embodiments.As described above, during harvesting, the articulated configuration ofheader 104 (in which left wing 144 a is hingedly attached to centersection 142 via a left hinge joint 146 a and in which right wing 144 bis hingedly attached to center section 142 via a right hinge joint 146b) allows the wings 144 of the header 104 to pivot upward and/ordownward relative to the center section 142 to allow the header 104 tomore closely follow the contours of the terrain.

As shown in FIG. 6A, to facilitate the ability of the wings 144 totravel over and follow contours in terrain during harvesting operation,the blocker valve 300 is in a flow configuration in which the flowstructure 302 of the blocker valve 300 is aligned between theaccumulators 206 and the attenuation hose 208 so as to allow fluid tofreely flow between the accumulators 206 and fluid cylinder 202. Asdescribed above, by allowing fluid to flow into and out from the fluidcylinder 202, the fluid cylinder 202 is able to extend and retract asneeded in response to changes in terrain. As will be understood,according to various embodiments, a float system configured to assistthe header 104 in adapting to changes in terrain (such as, e.g., bymonitoring changes in pressure imparted onto the header 104 andassisting in the flow of fluid into and out from the fluid cylinder 202so as to maintain a desired target pressure) may be incorporated intoharvester 100.

Because fluid is allowed to flow freely between the accumulators 206 andfluid cylinder 202 during harvesting operation of the device, thepressure within the attenuation hose 208 will be substantially the sameas the pressure within the accumulators 206. Additionally, because themass of the header 104 is supported by the ground during harvesting, asshown by FIG. 6B, the wings 144 extending substantially parallel toground. The simplified block diagram of FIG. 6B illustrates the header104 when the header 104 is positioned on substantially flat terrain, andas such, the entire header 104 is shown in FIG. 6B as extending in agenerally planar manner. However, as will be understood, if thesimplified block diagram of FIG. 6B were to represent the header 104along uneven terrain, the wings 144 of header 104 would be shown asextending substantially parallel to the terrain above which the wings144 extended, such that the wings 144 would extend at non-zero degreeangles relative to the center section 142.

Referring to FIG. 7A, a simplified diagram of the suspension system 200according to one embodiment is illustrated representative of atransition configuration of the harvester 100, in which the header 104is still supported by the ground (i.e. the header 104 has not beenelevated to a point where the combine 102 supports the entirety of theweight of the header 104) and in which the blocker valve 300 has beendeenergized or otherwise deactivated from the flow position to therestricted-flow position.

In the transition configuration, the switching of the blocker valve 300into the restricted-flow position prevents any fluid from flowing intoor out from the accumulators 206. Upon entering into the transitionconfiguration, the amount of fluid within the fluid cylinder 202 andattenuation hose 208 corresponds to the amount of fluid that had beenpresent within the fluid cylinder 202 and attenuation hose 208immediately prior to the blocker valve 300 being switched to therestricted-flow position. Accordingly, upon entering the transitionconfiguration, the wings 144 are ‘locked’ in their last position priorto the harvester 100 being put into the transition configuration. The‘locked’ configuration of the wings 144 may correspond to aconfiguration of the wings 144 in which one or both of the wings 144extend angled upward relative to center section 142, extend angleddownward relative to center section 142, and/or extend substantiallyparallel to center section 142. As will be understood, the configurationof the wings 144 in the ‘locked’ position will depend on whether thefluid cylinder 202 was in a retracted, expanded, or neutral stateimmediately prior to switching the blocker valve 300 into therestricted-flow configuration.

As illustrated in FIG. 7B, because the header 104 remains partiallysupported by the ground in the transition configuration, the wings 144of the header 104 remain extending in a direction substantially parallelto the terrain above which the wings 144 are supported. As similarlydescribed with reference to FIG. 6B, the header 104 that is representedby the simplified block diagram of FIG. 7B is shown in a configurationin which the header 104 is positioned atop substantially horizontalterrain. However, as will be understood, if the simplified block diagramof FIG. 7B were to represent the header 104 positioned along uneventerrain, the wings 144 of header 104 would be shown as extendingsubstantially parallel to the surface above which the wings 144 extend,such that the wings 144 would extend at non-zero degree angles relativeto the center section 142.

Referring to FIG. 8A, a simplified block diagram representative of thesuspension system 200 during non-harvesting transport of the harvester100 with the header 104 in an elevated position in which the weight ofthe header 104 is entirely supported by the combine 102 is shownaccording to one embodiment. As shown in FIG. 8A, in such an elevated,non-harvesting configuration of the header 104, the blocker valve 300remains closed in a restricted-flow configuration, in which flow offluid from the fluid cylinder 202 and attenuation hose 208 into theaccumulators 206 is prevented.

According to various embodiments, the attenuation hose 208 isconstructed with a desired degree of elasticity and resilience, whichallows the attenuation hose 208 to expand to hold increased volumes offluids as compared to an initial, neutral configuration of theattenuation hose 208. Although the flow of fluid into the accumulators206 is prevented by the blocker valve 300, fluid is free to flow betweenthe fluid cylinder 202 and attenuation hose 208 during the elevated,non-harvesting transport configuration of the header 104. As such, whenthe header 104 is elevated, causing the wing 144 to no longer besupported the ground, the elastic nature of the attenuation hose 208 isconfigured to allow some, or all, of the fluid that was ‘locked’ in thefluid cylinder 202 during the transition configuration (as describedwith reference to FIGS. 7A and 7B above) to flow into the attenuationhose 208, thereby increasing the volume of ‘locked’ fluid alreadypresent within the attenuation hose 208 (as also described withreference to FIGS. 7A and 7B above).

As representatively illustrated by the simplified block diagram of FIG.8A, the displacement of some or all of the fluid from the fluid cylinder202 into the attenuation hose 208 increases the pressure of the fluidwithin the attenuation hose 208 to a pressure that is greater than thepressure of the fluid stored within the accumulators 206. Meanwhile, asrepresentatively illustrated by the simplified block diagram of FIG. 8B,the decrease in the volume of fluid within the fluid cylinder 202resulting from the displacement of fluid from the fluid cylinder 202into the attenuation hose 208 decreases the ability of the fluidcylinder 202 to suspend the wing 144, which in turn causes the wing 144to pivot downward relative to the center section 142 by an angle of alfrom an initial wing 144 position defined by the position of the wing144 in the transition configuration (which in turn, corresponds to lastposition of the wing 144 during the last harvesting configuration of theheader 104 prior to the blocker valve 300 being switched to arestricted-flow position).

According to various embodiments, the angle α1 may range fromapproximately 0.05° to 1.5°, more specifically between approximately0.5° and 1.0°, and even more specifically between approximately 0.6° and0.8°. As will be understood, the angle α1 by which the left wing 144 ais pivoted downwards relative to the center section 142 during theelevated, non-harvesting transport configuration may be the same or maybe different than the angle α1 by which the right wing 144 b is pivoteddownwards relative to the center section 142 during the elevated,non-harvesting transport configuration.

Although, as shown in FIG. 8B, the wings 144 of the header 104 willexhibit some degree of sagging (i.e. pivoting of the wings 144 downwardsrelative to the center section 142), with respect to the initialposition of the wings 144 as defined by the position of the wings 144during the transition configuration, the position of the wings 144during the elevated, non-harvesting transport configuration may extendat an upwards angle relative to the center section 142, generally planarwith the center section 142, or at a downwards angle relative to thecenter section 142. As will be understood, the angle(s) relative to thecenter section 142 at which the wings 144 extend during the elevated,non-harvesting transport configuration will depend on factors includingthe angle(s) of the wings 144 relative to the center section 142 duringthe last harvesting configuration of the header 104 prior to the blockervalve 300 being switched to a restricted-flow position as well as theangle(s) al by which the wings 144 are pivoted downwards during theelevated, non-harvesting transport configuration.

According to various embodiments, as the harvester 100 is in theelevated, non-harvesting transport configuration (such as, e.g.,represented in FIGS. 8A and 8B), the harvester 100 may transition to adownward flex configuration in response to the mass of the header 104being subject to a downwards acceleration force (such as, e.g., inresponse to the harvester 100 travelling over uneven terrain). As such,the harvester 100 is subject to additional instantaneous loading in thedownward flex configuration in addition to the sustained loading thatthe harvester 100 is subject to during the non-harvesting transportconfiguration. As illustrated in FIG. 9A, during such additional loadingof the header 104 in the downward flex configuration, additional fluidflows out of the fluid cylinder 202 and into the attenuation hose 208.This additional fluid causes the volume of fluid within the attenuationhose 208 to further increase from the increased volume that theattenuation hose 208 was subject to during the elevated, non-harvestingtransport configuration. As shown in FIG. 9A, as a result of thisadditional fluid now held within the attenuation hose 208, the pressurewithin the attenuation hose 208 is further increased.

Meanwhile, as representatively illustrated by the simplified blockdiagram of FIG. 9B, the additional decrease in the volume of fluidwithin the fluid cylinder 202 as fluid is displaced from the fluidcylinder 202 and into the attenuation hose 208 during the downward flexconfiguration causes the wing 144 to pivot further downwards relative tothe center section 142 by an angle of α2. According to variousembodiments, the angle α2 may range from approximately 0.05° toapproximately 2.0°, more specifically between approximately 0.5° andapproximately 1.5°, and even more specifically by approximately 1.0°. Aswill be understood, the angle α2 by which the left wing 144 a is pivoteddownwards relative to the center section 142 during the downward flexconfiguration may be the same or may be different than the angle α2 bywhich the right wing 144 b is pivoted downwards relative to the centersection 142 during the downward flex configuration.

As explained with reference to FIG. 8B, although, as shown in FIG. 9B,the wings 144 of the header 104 will exhibit some degree of sagging(i.e. pivoting of the wings 144 downwards relative to the center section142), with respect to the position of the wings 144 in the configurationimmediately prior to the downward flex configuration of the header 104(such as, e.g., the elevated, non-harvesting transport configuration ofFIGS. 8A and 8B), the position of the wings 144 during the downward flexconfiguration may extend at an upwards angle relative to the centersection 142, generally planar with the center section 142, or downwardsrelative to the center section 142. As will be understood, the angle(s)relative to the center section 142 at which the wings 144 extend duringthe downward flex configuration will depend on factors such as, e.g.,the angle(s) of the wings 144 relative to the center section 142 duringthe last harvesting configuration of the header 104 prior to the blockervalve 300 being switched to a restricted-flow position; the angle(s) alby which the wings 144 are pivoted downwards during the elevated,non-harvesting transport configuration; the angle(s) α2 by which thewings 144 are pivoted downwards during the downward flex configuration;etc.

As illustrated by FIGS. 6A-9B, the ability of the blocker valve 300 toisolate flow into the accumulators 206 during a restricted-flow positionand to allow flow to and from the accumulators 206 during a flowposition provides the suspension system 200 with first and secondvariable states which selectively allow for differing degrees ofpivoting of the wings 144 relative to the center section 142. Asdiscussed with reference to FIGS. 6A and 6B, when the blocker valve 300is in the flow position, the first variable state is defined by thehydraulic circuit defined between the fluid cylinder 202, theaccumulators 206, and the attenuation hose 208. In this first variablestate, the ability of fluid to flow freely between the fluid cylinder202 and the accumulators 206, allows the wings 144 to pivot about thecenter section 142 by an amount that defines a first range of motion. Byallowing the wings 144 to pivot about the center section 142, thesuspension system 200 enables the wings 144 to dynamically adapt to andfollow terrain, which, in addition to increasing crop yield efficiency,also reduces the dynamic loads on the harvester 100 during harvestingoperation.

As discussed with reference to FIGS. 7A-9B, when the blocker is in therestricted-flow position, the second variable state is defined by thehydraulic circuit defined between the fluid cylinder 202 and theattenuation hose 208. In the second variable state, the expandablenature of the attenuation hose 208 allows the attenuation hose 208 tohold fluid that may flow out of the fluid cylinder 202. This ability ofthe attenuation hose 208 to hold an increased capacity of fluid providesthe suspension system 200 with a manner by which the wings 144 areprovided with a second range of motion by which the wings 144 may pivotrelative to the center section 142.

Because the second range of motion is smaller than the first range ofmotion (such as, e.g., by between approximately 10% and approximately30%), the ability of the wings 144 to pivot about the center section 142is more limited when the suspension system 200 is in the second variablestate than when the suspension system 200 is in the first variablestate. As such, when the header 104 is elevated from the ground with thesuspension system 200 in the second variable state (such as, e.g.,discussed with reference to the elevated, non-harvesting transportconfiguration shown in FIGS. 8A and 8B) the suspension system 200 isconfigured to maintain the header 104 in a relatively levelconfiguration in which the header 104 only exhibits a minimum amount ofsagging, thus minimizing the risk of the outermost ends of the wings 144inadvertently coming into contact with the ground during non-harvestingtransport of the harvester 100.

Although the range of motion through which the wings 144 are able topivot in the second variable state is limited, by providing even alimited range of motion by which the wings 144 are able to pivot aboutthe center section 142, (such as, e.g., by a range of betweenapproximately ±0.05° and approximately ±2.0°) the suspension system 200is able to reduce the mass of the header 104 that is accelerated duringtransport of the harvester 100 (such as, e.g., during when the harvesteris an the elevated, non-harvesting transport configuration), therebyreducing the stress on the structure of the combine 102 (such as, e.g.,by at least approximately 5%).

As noted above, the ability of the suspension system 200 to provide thewings 144 with a limited ability flex to while the suspension system 200is in the second variable state is provided by the ability of theattenuation hose 208 to hold fluid that flows out from the fluidcylinder 202 when the wings 144 are subject to downward forces (such as,e.g., when the header 104 is elevated entirely off of the ground in theelevated, non-harvesting transport configuration or during the downwardflex configuration in which the harvester 100 travelling with anelevated header 104 encounters uneven terrain). Accordingly, as will beunderstood, in various embodiments, the range of motion through whichthe wings 144 are able to pivot while the suspension system 200 is inthe second variable state may be varied by, e.g., changing the length ofthe attenuation hose 208, changing the selection of materials and/orstructure of the attenuation hose 208 (to either make the attenuationhose 208 more or less compressible), etc. Additionally, according tosome embodiments, the suspension system 200 may optionally be providedwith an additional structure via which fluid may be added to and/orremoved from the circuit defined by the fluid cylinder 202 and theattenuation hose 208 when the suspension system 200 is in the secondvariable state.

As will be understood, although the harvesting configuration of FIGS. 6Aand 6B, the transition configuration of FIGS. 7A and 7B, the elevated,non-harvesting transport configuration of FIGS. 8A and 8B, and thedownward flex configuration of FIGS. 9A and 9B have been described asoccurring in a sequential manner, the various configurations illustratedand described with reference to FIGS. 6A-9B may occur according to anyother number of sequences, in which any of the configurations may berepeated any number of different times. Additionally, the header 104 maybe subject to the configurations of FIGS. 6A-9B for varied durations oftime. For example, according to various embodiments, the downward flexconfiguration of FIGS. 9A and 9B may directly follow the transitionconfiguration of FIGS. 7A and 7B. In some embodiments, the transitionconfiguration of FIGS. 7A and 7B may directly follow the elevated,non-harvesting transport configuration of FIGS. 8A and 8B.

Referring now to FIGS. 10A-10B, a simplified block diagram of thesuspension system 200 and the header 104 configuration is shown duringan upward flex configuration of the harvester 100. In some embodiments,FIGS. 10A-10B represent an upward flex configuration caused by theheader 104 encountering uneven terrain. For example, header 104 mayexperience transient negative loading (i.e., negative as in the oppositeof the load caused by gravity) when riding over a divot or whenreturning to level ground after riding over a bump. In some embodiments,the upward flex configuration occurs subsequent a downward flexconfiguration, described above with reference to FIGS. 8A-9B. In otherembodiments, FIGS. 10A-10B represent an upward flex configuration causedby transient negative loading due to flexure of a trailer upon which theheader 104 is supported during a transport operation.

As representatively illustrated by the simplified block diagram of FIG.10A, negatively loading the header 104 results in the displacement ofsome fluid from the attenuation hose 208 into the fluid cylinder 202.This displacement decreases the pressure of the fluid within theattenuation hose 208 to a pressure is that is less than the pressure ofthe fluid stored within the accumulators 206. Because the blocker valve300 is in the restricted-flow position, the orificed check valvestructure 400 prevents flow in the direction from the fluid cylinder 202through the attenuation hose 208 and into the accumulators 206 whilepermitting some limited/metered flow of fluid from the accumulators 206to the attenuation hose 208 and into the fluid cylinder 202. Forexample, the limited/metered flow rate of fluid through the orificedcheck valve structure 400 may be substantially less than the flow rateof fluid when the blocker valve 300 is in the flow configuration (i.e.,the configuration depicted in FIG. 6A).

Meanwhile, as representatively illustrated by the simplified blockdiagram of FIG. 10B, the increase in the volume of fluid within thefluid cylinder 202 resulting from the displacement of fluid from theattenuation hose 208 into the fluid cylinder 202 increases the abilityof the fluid cylinder 202 to lift the wing 144, which in turn causes thewing 144 to pivot upward relative to the center section 142 by an angleof α3 from an initial wing 144 position. However, the presence of theorificed check valve structure 400 in the blocker valve 300 constrainsthe angle α3 by which the wing 144 is permitted to pivot relative to thecenter section 142. By contrast, unmetered flow from the accumulators206 to the attenuation hose 208 may result in unconstrained andpermanent ratcheting of the wings 144 into an upward configuration.Permanent ratcheting of the wings 144 into the upward configuration isundesirable, as it may degrade the harvesting efficiency of the header104 and may overload the center section 142 of the header 104, resultingin damage to the center section 142 or decoupling of the header 104 fromthe trailer during a transport operation.

According to various embodiments, the angle α3 may range fromapproximately 0.05° to 1.0°, and more specifically between approximately0.1° and 0.5°. The angle α3 may be constrained by the restricted flowthrough the orificed check valve structure 400 and the compliance of theattenuation hose 208. As will be understood, the angle α3 by which theleft wing 144 a is pivoted upwards relative to the center section 142during the upward flex configuration may be the same or may be differentthan the angle α3 by which the right wing 144 b is pivoted upwardsrelative to the center section 142 during the upward flex configuration.

Referring now to FIG. 11, an agricultural harvesting header 104 in anintegrated transport configuration is depicted, according to someembodiments. As shown, the integrated transport configuration of theheader 104 includes integrated transport structural members 502 and aplurality of ground engaging wheels 504 that support the header 104 andapply a sustained negative load to the left wing 144 a and the rightwing 144 b such that the left wing 144 a and the right wing 144 b areforced into an upward flex configuration. Turning now to FIGS. 12A-12B,a simplified block diagram of the suspension system 200 and the header104 configuration is shown during an integrated transport configurationof the harvester 100. In some embodiments, the integrated transportconfiguration of the harvester 100 is identical or substantially similarto the integrated transport configuration depicted in FIG. 11.

As depicted in the simplified block diagram of FIG. 12A, the upwardforce on the wings due to the integrated transport structure results inthe displacement of some fluid from the attenuation hose 208 into thefluid cylinder 202. This displacement decreases the pressure of thefluid within the attenuation hose 208 to a pressure that is less thanthe pressure of the fluid stored within the accumulators 206. Becausethe blocker valve 300 is in the restricted-flow position, the orificedcheck valve structure 400 prevents flow in the direction from the fluidcylinder 202 through the attenuation hose 208 and into the accumulators206 while permitting some limited/metered flow of fluid from theaccumulators 206 to the attenuation hose 208 and into the fluid cylinder202 until the pressure in the accumulators 206 and the attenuation hose208 is equalized. As described above, the limited/metered flow rate offluid through the orificed check valve structure 400 may besubstantially less than the flow rate of fluid when the blocker valve300 is in the flow configuration (i.e., the configuration depicted inFIG. 6A).

Meanwhile, as representatively illustrated by the simplified blockdiagram of FIG. 12B, the increase in the volume of fluid within thefluid cylinder 202 resulting from the displacement of fluid from theattenuation hose 208 into the fluid cylinder 202 increases the abilityof the fluid cylinder 202 to lift the wing 144, which in turn causes thewing 144 to pivot upward relative to the center section 142 by an angleof α4 from an initial wing 144 position. However, the presence of theorificed check valve structure 400 in the blocker valve 300 constrainsthe angle α4 by which the wing 144 is permitted to pivot relative to thecenter section 142 and prevents the fluid cylinder 202 from pulling avacuum on the attenuation hose 208, which may result in decreaseddurability of the header 104.

According to various embodiments, the angle α4 may range fromapproximately 1.0° to 10.0°, and more specifically between approximately3.0° and 7.0°. The angle α4 may be constrained by a physical limitationof the fluid cylinder 202. For example, in some embodiments, the fluidcylinder 202 includes a cylinder rod slidably coupled to a cylinderbarrel, with the wing 144 coupled to the cylinder rod. Thus, the angleα4 is limited by an amount the cylinder rod is permitted to protrudefrom the cylinder barrel. As will be understood, the angle α4 by whichthe left wing 144 a is pivoted upwards relative to the center section142 during the upward flex configuration during integrated transport maybe the same or may be different than the angle α4 by which the rightwing 144 b is pivoted upwards relative to the center section 142 duringthe integrated transport configuration.

As will be understood, although the articulated header 104 illustratedherein has been shown as comprising three sections: a center section142, a left wing 144 a, and a right wing 144 b, according to otherembodiments, the articulated header 104 may comprise any number ofdifferent sections, including, e.g., a two section arrangement definedby only the left wing 144 a and the right wings 144 b.

The construction and arrangement of the systems and methods as shown inthe various exemplary embodiments are illustrative only. Although only afew embodiments have been described in detail in this disclosure, manymodifications are possible (e.g., variations in sizes, dimensions,structures, shapes and proportions of the various elements, values ofparameters, mounting arrangements, use of materials, colors,orientations, etc.). For example, the position of elements may bereversed or otherwise varied and the nature or number of discreteelements or positions may be altered or varied. Accordingly, all suchmodifications are intended to be included within the scope of thepresent disclosure. The order or sequence of any process or method stepsmay be varied or re-sequenced according to alternative embodiments.Other substitutions, modifications, changes, and omissions may be madein the design, operating conditions and arrangement of the exemplaryembodiments without departing from the scope of the present disclosure.

What is claimed is:
 1. A wing locking system for a harvesting headercomprising: an accumulator; a fluid cylinder operably attached to a wingof a harvesting header; a hose fluidly connecting the accumulator andthe fluid cylinder; and a valve operably disposed between theaccumulator and the fluid cylinder, the valve having a first selectableposition configured to permit a first fluid flow rate between theaccumulator and the fluid cylinder and a second selectable positionconfigured to permit a second fluid flow rate from the accumulator tothe fluid cylinder; wherein the first fluid flow rate is greater thanthe second fluid flow rate.
 2. The wing locking system of claim 1,wherein the second selectable position of the valve permits fluid flowfrom the accumulator to the fluid cylinder through an orificed checkvalve and prevents fluid flow from the fluid cylinder to theaccumulator.
 3. The wing locking system of claim 1, wherein, when thevalve is in the second selectable position, the flow of fluid into thefluid cylinder is configured to constrain an upward pivot angle of thewing.
 4. The wing locking system of claim 3, wherein the valve is in thesecond selectable position when the harvesting header encounters anegative loading condition.
 5. The wing locking system of claim 4,wherein the upward pivot angle of the wing ranges from 0.05° to 1.0°. 6.The wing locking system of claim 3, wherein the valve is in the secondselectable position when the harvesting header is in an integratedtransport configuration.
 7. The wing locking system of claim 6, whereinthe upward pivot angle of the wing ranges from 1.0° to 10.0° and isconstrained by a limitation of the fluid cylinder.
 8. A method ofoperating a harvesting header comprising: providing a harvesting headercomprising: a center section; a left wing hingedly attached to thecenter section; a right wing hingedly attached to the center section;and a wing locking system comprising: an accumulator; a fluid cylinderoperably attached to at least one of the left wing and the right wing; ahose fluidly connecting the accumulator and the fluid cylinder; and avalve operably disposed between the accumulator and the fluid cylinder,the valve having a first selectable position configured to permit afirst fluid flow rate between the accumulator and the fluid cylinder anda second selectable position configured to permit a second fluid flowrate from the accumulator to the fluid cylinder; wherein the first fluidflow rate is greater than the second fluid flow rate; and operating thevalve in the second selectable position during at least one of atransient negative loading condition and a sustained negative loadingcondition caused by an integrated transport configuration of theharvesting header.
 9. The method of claim 8, wherein the secondselectable position permits fluid flow from the accumulator to the fluidcylinder through an orificed check valve and prevents fluid flow fromthe fluid cylinder to the accumulator.
 10. The method of claim 8,wherein the flow of fluid from the hose into the fluid cylinder causesat least one of the left wing and the right wing to pivot upwardsrelative to the center section by between approximately 0.05° andapproximately 1.0° during the transient negative loading condition ofthe harvesting header.
 11. The method of claim 8, wherein the flow offluid from the hose into the fluid cylinder causes at least one of theleft wing and the right wing to pivot upwards relative to the centersection by between approximately 1.0° and approximately 10.0° during thesustained negative loading condition caused by the integrated transportconfiguration of the harvesting header.
 12. The method of claim 8,wherein, when the valve is in the first selectable position, the flow offluid into the fluid cylinder and out of the fluid accumulator and outfrom the fluid cylinder and into the fluid accumulator is configured toallow the fluid cylinder to move the at least one of the left wing andthe right wing within a first range along a wing trajectory and when thevalve is in the second selectable position, the flow of fluid out fromthe fluid accumulator into the fluid cylinder is configured to allow thefluid cylinder to move the at least one of the left wing and the rightwing within a second range along the wing trajectory, the second rangebeing smaller than the first range.
 13. ‘The method of claim 8, whereinthe transient negative loading condition is caused by uneven terrain.14. The method of claim 8, wherein the transient negative loadingcondition is caused by flexure of a trailer transporting the harvestingheader.
 15. The method of claim 8, wherein, when the harvesting headeris in the integrated transport configuration, the harvesting header issupported by a plurality of structural members and a plurality of groundengaging wheels.
 16. A harvester system comprising: a center section; aleft wing hingedly attached to the center section; a right wing hingedlyattached to the center section; and a wing locking system comprising: anaccumulator; a fluid cylinder operably attached to at least one of theleft wing and the right wing; a hose fluidly connecting the accumulatorand the fluid cylinder; and a valve operably disposed between theaccumulator and the fluid cylinder, the valve having a first selectableposition configured to permit a first fluid flow rate between theaccumulator and the fluid cylinder and a second selectable positionconfigured to permit a second fluid flow rate from the accumulator tothe fluid cylinder; wherein the first fluid flow rate is greater thanthe second fluid flow rate.
 17. The harvester system of claim 16,wherein the second selectable position of the valve permits fluid flowfrom the accumulator to the fluid cylinder through an orificed checkvalve and prevents fluid flow from the fluid cylinder to theaccumulator.
 18. The harvester system of claim 16, wherein the flow offluid from the hose into the fluid cylinder causes at least one of theleft wing and the right wing to pivot upwards relative to the centersection by between approximately 0.05° and approximately 1.0° during atransient negative loading condition.
 19. The harvester system of claim16, wherein the flow of fluid from the hose into the fluid cylindercauses at least one of the left wing and the right wing to pivot upwardsrelative to the center section by between approximately 1.0° andapproximately 10.0° during a sustained negative loading condition causedby an integrated transport configuration of the harvesting header. 20.The harvester system of claim 19, wherein the harvester system furthercomprises a plurality of structural members and a plurality of groundengaging wheels.